Fluid pressure brake means



March 25, 1941. E. E. HEWITT FLUID PRESSURE BRAKE MEANS Filed Nov. 30, '1939 Rb mw wb NQ b5 Mm; Q m

INVENTOR ELLIS E.HEWITT ATZIORNEY Patented Mar. 25, 1941 UNITED STATES PATENT OFFICE 1 2,2se,2'6s I FLUID PRE SSURE'BRAKE- MEAN S Ellis E, Hewitt, Edgewood, Pa., assignor to The Westinghouse'AirBrake Company, Wilmerding, I Pa., a corporation of Pennsylvania. Application November 30, 1939, Serial No. 306,893

Il'Claim's. (Cl. 303-221 This invention relates to fluid pressure-brakes for railway vehicles and more particularly to the type in which the degree with which'the brakes on the vehicle or vehicles of a train are applied is varied in accordance with the speed or rate at which the vehicle or train is traveling.

In PatentNo. 2,140,624, issued-to me on December 20, 1938, there is disclosed a fluid pressure brake equipment of the above type which' em- 10 bodies a speed governor device and arelay valve device. The relay valve device is provided for controlling the application and release of brakes on a vehicle and is so constructed and arranged for control by said speed governor device as to operate to limit the degree with which the brakes on the Vehicle are applied in accordance with the speed at which the vehicle is operating. By thus limiting the degree with which the brakes can be applied on'the vehicle, slipping or sliding of 20 the. vehicle Wheels is greatly minimizedat all times.

The principal object of the present invention is to provide a fluid pressure brake equipment embodying an improved speed controlled relay 5 valve device of the above generaltype.

Other objects and advantages will-be apparen from the following more detailed description of the invention.

Description of parts In the accompanying drawing,.the single figure is a diagrammatic view, namely insection, of a fluid pressure brake equipment embodying the invention. 7 i 35 As shown in the drawing, thefluid pressure brake equipment comprises a brake'application control or relay valve device I, a brake valve device 2, a speed governor or speed responsive switch device 3, a switch device 4, a brake cylinder device 5, a main reservoir 6 and a feed valve device I. r

The brake application control-or rela valve device I comprises a brake application and release valve device 9, a diaphragm, portion I associated with said device for controlling the operation thereof, an associated magnet valve device portion II for controlling the operation of said diaphragm portion, andan inshot valve device or pressure limiting device associated 50 with the magnet valve device portion II The application and release valve device 9 comprises a casing having .a chamber I3 which is connected to a secondary control-pipe I4 leading, in the present embodiment of the invention,

to the brake cylinder device 5. In theta-sin there is provided a brake application valve I5 for controlling a supply of fluid under pressure to chamber I3 and thereby to the brake cylinder device 5, and a brake release valve I6 for releasing fluid under pressure from said chamber 5 and thereby from the brake cylinder device 5 to the atmosphere.

The application valve I5 is preferably of the valve piston typelhaving at one side a chamber 1 I which is connected through a passage I8 to a 10 pipe I9 leading tothe delivery side of the feed valve device I; the other side of said feed valve device being connected to a pipe I85 leading to the main reservoir 6 and through which said reservoir is also connected to the brake valve device 2. At the opposite side ofvalve piston I5 there isprovided aichamber which is connectedthrough a port 2|, having a relatively restricted flow area, to the passage III. In the casing there 'isprovided a valve seat 22 adapted to 20 be engaged by the application valve I5 for closing communication between chambers I1 and I3. Sin-chamber 20 there is provided a relatively light bias spring 23acting on the application valve I5 for normallyurging itinto engagement with the 25 valve seat 22. 5

The application'valve I5 is provided'with an axial bore for" connecting chamber 20 to chamber I 3 and slidably mounted in this bore is the fluted stem ofa pilot'valve 25 which is disposed in 3 chamber 20 'and adapted to engage or seat against the application valve forclosing com- 'munication from said chamber to the chamber I3. A light bias spring 26 is provided in chamber 20within'thespring 23 and acts on the pilot valve 25Ifor' normally urging it to its closed position; i V ,In' the casing there is provided an outstanding shelf -21a having a bore in coaxial alignment with: the pilot valve stem 24, and slidably mount- 40 ed in this bore is an operating pin 21. The end of this pin' adjacent the'pilo-t valve stem 24 is adaptedupon movement in one direction in the casing to successively operate or unseat first the pilot valve 25 and then engage' and unseat the '45 application valve I5. The application valve I5 is provided'with a slot' in its seating face to preventrclosing communication past the pilot valve stem 24 to chamber I3 when pin 21 is in engagement Withsaid' valve; 5

The release valve I6 is disposed in the casing at one side of the application valve I5 wit-hits axis parallel to; thatof said application valve." The release valve I6 comprises a piston '28, a1 valve ZS adapted "to engage" a seat 30" formed 'in' the casing for closing communication between chamber I 3 and an atmospheric release port 3|, and a stem 32 connecting said piston and valve together.

The release valve piston 28 is slidably mounted in a suitable bore in the casing and has at one side a chamber 33 and at the opposite side a chamber 34 which is open to the atmospheric vent passage 31. The valve 23 is contained in the chamber l3 and a bore 35 i provided connecting chamber 34 to the seat 30 for said valve. The valve stem 32 extends through the bore '35 and is provided with one or more suitable guides 32a engaging the side wall of said bore for sup: porting the release valve 28 in operating alignment with its seat 36 and past which guides come munication is adapted to be established between chambers 3 and 34 when the release valve 28 is unseated.

The release valve I6 is provided with an axial bore connecting chamber |3 to chamber 33. In chamber l3 there is provided a pilot valve 36 for the release valve l6 and said pilot Valve has a stem 31 loosely extending through the bore in the release valve and into chamber 33 wherein a nut 38 is provided on the end of the stem. The nut 38 is of greater diameter than the bore through the release valve so as to engage the outer face of the piston 28, a slot 39 being pro?- vided in said face for maintaining communication between the chamber 33 and the bore in the release valve under such conditions.

The casing is provided with a shelf 40 extending into chamber I3 and in this shelf there is provided a bore in coaxial alignment with the release valve l6. An operating pin 4| is slidably mounted in thisbore and is provided on its left hand end with an annular rib 42 encircling the pilot valve 36 and adapted to engage a like rib 43 on said valve for unseating said valve upon movement of said pin in the direction of the right hand.

Operation of the application valve l5 and re? lease valve I6 and of the pilot valves 25 and 36, respectively, is adapted to be controlled by a floating lever 44 provided in chamberl3. .This lever is pivoted intermediate its ends by a hearing 45, shown as of a ball-bearing type, on apin 46 which is carried by a plunger 41. The plunger has on one end a piston-like guide 48 which is slidably mounted in a bore 49 formed .between the valve operating pins 21 and 4|.

The floating lever 44 is arranged with one end engaging the operating pin 21 and the other end engaging the operating pin 4|. At the side of the lever 44 opposite that engaged by the operating pin 21 there is provided in the casing a stop screw 56 adapted to be engaged by the lever when the application valve I5 and the pilot valve 25 are in their seated positions shown. The operating pin 4| at the opposite side of plunger 41 is provided on the end opposite that connected to the release pilotvalve 36 with a portion 5| of reduced diameter connecting the pin to a plunger 52 which is slidably mounted in the casing. A pair of spaced shoulders 53 are thereby formed and between said shoulders and straddling the portion 5| of the operating pin is disposed the adjacent bifurcated end of lever 44. A light bias spring 54 is provided which acts on the plunger 52 urging same in the direction of the release pilot valve 36.

The diaphragm portion ID of the relay valve device comprises a casing secured to that of the application and release valve device 9 and in said casing there are provided four flexible diaphragms 55, 56, 51 and 58 arranged in coaxial relation with the plunger 41. These diaphragms are all spaced from each other and have successively reduced pressure areas, in the order named, the diaphragm 55 of greatest area being adjacent the application and release valve device 9.

At the left hand side of the largest diaphragm 55 there is provided a chamber 59 which is open to chamber l3 through a bore 66. The plunger 41 extends through the bore 6|] and in chamber 59 is provided with an integrally formed follower or pressure plate 6| having one face engaging the diaphragm 55. At the opposite side of diaphragm 55 there is provided a chamber 62 containing a pressure plate 63 which is mounted against the right hand face of diaphragm 55. A stud and nut 64 are provided securing the plates 6|. and 63 together and against the opposite faces of diaphragm 55. The plunger 41 is hus. supp rted at ne en by the guide pi ton 483 1 1 Qt the, other endv by the diaphragm 55 thereby providing a positively movable structure and one which will move upon slight differentials between pressures in chambers 59 and 62. A light bias spring 65 in chamber 59 is arranged to act on plunger- 41 for urging same in the direction of the right hand, for reasonswhich will later be brought out.

In chamber- 62 there is provided a combined follower plate and strut 66 of smaller diameter than follower 6| and having a disc like end piece 61 engaging the left hand side of the diaphragm 56 anda cylindrical portion 68, extending from said end piece and. engaging the pressure plate 63 secured to diaphragm. 55. The end piece 61 is provided in its outer face with an annular groove. and on theradjacent face of the diaphragm 56 there is provided an annular rib which fits into said groovefor holding, the follower 66 in operating relation with said diaphragm.

Between the diaphragms 5.6 and 51 there is provided a chamber 69 which contains a combined follower plate and strut 10 of smaller diameter but of the same, construction as the followerplatejfiiand connecting the adjacent faces of said diaphragms. A chamber 1| is formed between the diaphragms 51 and 58 and contains a combined follower plate and strut 12 similar to those above described and connecting said diaphragms. Atvthe outer face of the diaphragm 58-there is provided a chamber 13 containing a bias spring 14 which acts through a plate 15 against the adjacent face of the diaphragm 58, saidpl-ate being supported in coaxial relation with said diaphragmon a boss 16 projecting from the adjacent face-of the diaphragm.

The outer-end of thespring 14 is supported in 'a cap nut 18 having screw-threaded engagement with the casing. This permits assembling of the spring 14 in its operating position after the other'parts of the mechanism are assembled so as to thereby-- facilitate such assembly.

The pressure'ofspring 14 is less than'that of spring 65 so that the lattermaymaintain the diaphragmsin their normal or release positions, shown in the drawing. The only purpose of spring 14 is to coact with spring 65 to hold the several diaphragms and the followers interposed between in engagement with each other to avoid rattling pr shaking of the parts when the brakes on the vehicle are released and the several chambers; at the opposite sides jofthe diaphragms are atatmos her ic pressure, as will be laterdescribed.

and 8. low speed tained in a chamber 86 which is connectedto-a' primary control pipe 81 and is adapted to control communication between saidchamber and a chamber 88 which is connected through passages 89 and 98 to the diaphragmchamber 62. The valve 84 is contained in a chamber 9| which is connected through a choke 92 to a brake release passage 93, said valve being provided for controlling communication between said chamber and the chamber 88. The valves 84 and 85 are so arranged that upon energization of the electromagnet 83 the valve 84 will be seated and the valve 85 will be unseated. A spring 94 is provided which acts on the valve 85 for seating said valve and for unseating the valve 84 upon deenergization of the electro-magnet 83.

The medium speed magnet valve device 8I comprises an electro-magnet 95 and a pair of oppositely seating valves 96 and 91. The valve 91 is' contained in a chamber 98 which is connected to the primary control pipe 81 and'is provided for controlling communication between said chamber and a chamber 99 which is connected through passages I88 and IM to the diaphragm chamber 69. The valve 96 is contained in a chamber I82 which is connected to the release passage 93 through a choke I83, said valve being provided for controlling communication between said chamber and the chamber 99. The electromagnet 95 is operative upon energization' to seat the valve 96 and to unseat the valve 91. A spring I84 is provided acting on the valve 91 for seating same and for unseatingthe valve 96 upon deenergization of electro-magnet 95.

The low speed magnet valve device 82 com-' prises an electro-magnet I81 and a pair of oppositely seating valves I88 and I89 both of which are contained in a chamber II8 which is connected by way of passages III and H2 to the diaphragm chamber H. The valve I88 is provided for controlling communication between the chamber H8 and a chamber 3 which is connected through a choke II 4 to the release passage 93. The valve I89 is provided for controlling communication between ohamber H8 and a chamber II5 which is connected to the primary control pipe 81. Energization of the electromagnet I81 is adapted to effect unseating of the valve I88 and seating of the valve I89, while a spring II6 acting on the stem of the latter valve is adapted to operate upon deenergization of said electro-magnet to unseat the valve I89 and to seat the valve I88.

In the diaphragm portion of the relay valve device there are provided three chambers H1, H8 and H9 which are connected together by passages I28 and I2I. The chamber H1 is connected to a passage I22 which leads to the primary control pipe 81, while the chamber H9 is connected to a passage I23 leading to the diaphragm chamber 13.

A check valve I24 is provided in chamber II1 for normally closing communication between said chamber and passage 98 leading to the diaphragm chamber 62. This check valveis subject ,to the pressure of a light seating spring I25'which is magnet valve device 88,. a medium adapted to permit unseatin'g of the check valve upon release of fluid under pressure from said chamber to permit the release of fluid under pressure from passage 98 by way of said chamber. In chamber II8 there is provided a similar check valve I26 and spring I21 for controlling a release communication between passage I88 and said chamber. A similar check valve I28 and spring I29 are provided in chamber II9 to control a release communication between passage I I2 and said chamber.

The inshot valve device I2 comprises a casing secured to the magnet valve portion II of the relay valve device and containing a flexible diaphragm I38, an inshot or supply valve I3I at one side of said diaphragm, and a combined limiting and brake release valve I32 at the opposite side of said diaphragm, both of said valves being of the poppet type and arranged for control by said diaphragm.

The diaphragm I38 has at one side a chamber I33 which is connected through a bore I34 and a port I35 to the brake release passage93. At the opposite side of the diaphragm there is provided a chamber I36 which is open to the atmosphere through a vent. port I31.

The inshot valve I3I is contained in a chamber I38 which is connected to the primary control pipe 81 and is provided with a fluted stem I39 extending through a suitable bore in the casing and engaging a follower I48 disposed in chamber I33 and secured to one faceof the diaphragm I38. A light bias spring MI in chamber I38 acts on the inshot valve I3I for urging it. toward its seated position. i

A follower I42 disposed in chamber I36 is secured to the diaphragm I38 for movement therewith. This follower is provided with an operating stem I43 which extends through a suitable bore in the casing into a chamber I44 which is open to the vent pasage I31, communication being established between the chambers I36 and I44 through a breather port- I45 provided in the casing along the stem I43. In the chamber I36 and encircling the stem I43 there is provided a spring I45 which acts on the follower I42 urging the diaphragm I38 in the direction for unseating the inshot valve I3I. This spring is designed to provide a suflicient pressure on the diaphragm I38 to prevent movement thereof against the spring until a certain desired degree of fluid pressure is obtained in chamber I33, such as seven pounds per square inch.

The brake release valve I32 is contained in a chamber I46 which is connected to the brake release passage 93. This valve is provided with a fluted stem extending through a suitable bore in the casing into chamber I44 in coaxial relation with the diaphragm operated stem I43. A spring I41 in chamber I46 acts on the release valve I32 forurgingit to its seated position shown in the drawing. The release valve I32 is adapted to be unseated by the diaphragm stem I43 upon deflection of the diaphragm I38 in an upwardly direction and subsequent to seating of the inshot valve I3IbyspringI4I.

In the drawing it will be noted that the valve I3I is shown in its unseated position and the valve I32 in its seated position and it will also be noted that there is a slight space between the end of the operating stem I43 and the end of the stem depending from the release valve I32. This space is slightly greater than the distance through seated position so as to thereby insure that both valves will not be open at the same time.

The primary control pipe 81 is provided for conveying fiuid under pressure to the relay valve device I for efiecting an application of the brakes on a. vehicle and through which fluid .under pressure is adapted to be released .from'said' relay valve device to release the brakes on a vehicle. Such supply and release of fiuidunder pressure to and from the'prii'nary control pipe BTmaybe effected in any desired manner, as by the operation of the brake valve device 2. Theebrake valve device 2 may be of any suitable design, such as of the well known self-lapping type and which is providedwith a handle M8 for operabe of any suitable structure and is illustrated as comprising a casing I50 adapted to be mounted in any desired location on the body of the vehicle. and having a chamber I5l containing a centrifuge I52 which is provided for operating a switch device I53.

The centrifuge I52 comprises a rotary mem ber I56 carried on the end of a shaft I55 which is journaled in the casing and which is adapted to be rotated at a speed proportional to the i speed or rate of travel of the vehicle, in any suitable manner, such as of by way of a connection (not shown) with a car wheel or with the axle thereof.

The rotary member l54 carries a pair of bell crank levers I56 disposed opposite to each other at the opposite sides of the axis of said member. Each of the bell crank levers I56 is provided at its outer end with a governor weight I51 while the inner end of each of said levers engages the lower face of a collar I 58 secured to the lower end of an operating stem I59 of the switch device I53. In chamber I5I there is provided a spring I66 acting on the collar I58 which is adapted to yieldingly urge the operating stem I59 in a downward direction against the action of centrifugal force on the governor weights I51.

The upper part of the casing I50 is broken away to show three pairs of fixed contact fingers I60, I6I and I52. The operating stem I59 carries three movable contact members I63, I64 and I65 for engaging the pairs of contact fingers I60, I6I and I62, respectively, in bridging or circult-closing relation.

The contact I 63 is secured to the operating stem I59 under the contact fingers I60 and for movement with said stem, while the contacts I64 and I 65 are slidably mounted on said stem between the contact fingers I6I and I62. The stem I59 is provided between the contacts I64 and I65 with a collar I61 secured to the stem. A spring I68 engaging one side of collar I61 acts on the contact I64 urging it in the direction of another collar I69 provided on the stem. A spring I10 acts against the opposite face of collar I61 and on the contact l65 for urging it to-- ward a collar I1I provided on the stem I59.

It will be evident that as the shaft I55 is rotated' from the wheel or axle of a vehicle truck ata speed proportional to the rate of travel of the vehicle the action of centrifugal force on -magnet aeaaass the centrifuge weights I51 against: the opposing-force of'spring'l66' on collar I 58 will positionuthe stem I59 in various vertical positions depending upon the degree of vehicle speed. The partsare so'design'ed as to obtain the position shown in' the drawing with the contact I63 engaging or' bridging the contact fingers I60 and with the contact I64 engaging contact fingers I6I whenever the speed of the vehicle exceeds a' certainrelatively high degree or limit, such as 60 miles per hour. When the speed of the vehicle is below this high speed limit, the contact I63 will bedisengaged from the contact fingers I60. The pressure of biasing spring I68 will yieldinglyretain the contact I64 in engagement with the contact fingers I6I over a range of vehicle speedbetween said high speed limit and a medium speed limit, such as 40 miles per hour. Below this medium speed limit the collar I69 will disengage contactI64 from contact fingers I GI The contact I65 will be supported by the collar I1I in a-position out of engagement with the contact fingers I62 whenever the speed of the vehicle exceeds a certain low speed limit, such as 20-miles per hour. low speed limit the contact I65 will be in engagement with the contact fingers I62.

The pneumatic switch device 4 comprises a casing containing a piston I15 having at one side a pressure chamber I16 connected to the the piston I15 for urging same in the direction of chamber I16.

The piston I15 is provided with an operat-- ing stem, I carrying at its outer end a contact I8'I. A pair of stationary contact fingers I82 are arranged to be engaged by the contact I8I uponmovement thereof by piston I15 when fluid under pressure is supplied to the pressure chamber I16. One of the contact fingers I82 is connected to a wire I83 leading to any suitable source of electric current on the vehicle such as. to one terminal of a battery I84, the other terminal of which is grounded. The other contact. finger I82 is connected to a. wire I86 which leads. to the switch device I53 in the speed governor device 3 wherein said wire is connected to one of the contact fingers I60, one of'the contact fingers NH and one of the contact fingers I62.

The other contact finger I60 in the speed governor device is connected to one terminal of the high speed electro-magnet 83, the other terminal of which is grounded. The other contact finger I6I in the speed governor device is connected to one terminal of the medium speed electro-magnet 95 and the other terminal of this magnet is grounded. The other contact finger I62 in the speed governor device is connected to one side of the low speed electro- I'01 which has its other terminal grounded.

The main reservoir 6 is adapted to be supplied with. fluid under pressure in any conventional manner. The fluid under pressure thus supplied to the main reservoir 6 is adapted to flow to pipe I leading to the brake valve device 2 and to the feed valve device 1.

The feed-valve device I is provided for controlling the supply-of fluid under pressure from pipe I85 to'pipe I9 and is operative in the'usual manner t'o reduce thepressure of'fluid supplied At and below the .electro magnet I01 .015 thelow speed magnet to the, pipe I9 to a desired relatively low degree for supply to the application valve chamber H in the application and release valve'device 9. With the application valve 15 in its normal or seated position shown in the drawing the fluid pressure obtained in chamber l1 and acting on one face of the application valve I is adapted to equalize through port 2| into chamber 20 at the opposite side of the application valve and to thus permit spring 23 to hold the application valve in its closed position. I

Operation In operation, let it be assumed that the brakes on the vehicle are released. Under this condition the primary control pipe 81 will be void of fluid under pressure and all parts of the relay valve device 2, the speed governor device 3 and of the pneumatic switch device 4'will be in the positions shown in the-drawing. When in this condition the several diaphragm chambers in the relay valve device will be vented by way of the primary control pipe 81 and brake valve device 2, as will be hereinafter more fully brought out, and this condition permits the spring 65 to hold the several diaphragms and the plunger 41 in the positions shown. With the plunger 41 and floating lever 44 thus positioned, the application valve I5 will be seated toprevent flow of fluid under pressure from chamber I1 to chamber I3 and the release valve 29 will be unseated connecting chamber I3 to the vent port 3|, whereby the secondary control pipe I4 andthereby the brake cylinder device 5 will be open to the atmosphere and void of fluid under pressure. The application valve .15 will be seated as above described due to the action of spring 23 since the fluid pressures in Chambers [1 and 20 will be equalized through port2l. Likewise pilot valve 25 will be seated by spring 26.

With the vehicle operating at or above the high speed limit, such as 60 miles per hour, if-it is desired. to apply the brakes on the vehicle, the brake valve device 2 is operated in the usual manner to supply fluid to the primary control pipe 81 at whatever pressure is requiredfor providing a chosen rate of deceleration of the vehicle. l

The fluid under pressure supplied to the primary control pipe 91 flows to piston chamber 116 in the'switch device 4 and when a certain relatively low pressure is thus obtained in said chamber, said presure acting on piston I moves said piston against spring I19 and thereby shifts the contact l8l into engagement with the contact fingers I82. The battery I04 is thereby connected to wire I86 and to one of each pair of fingers I60, I6I and I62 in the speed governor device 3.

With the speed governor device 3 in the high speed position shown in the drawing,"the contacts I63 and I64 are in their circuit-closing positions, so that electric current supplied from the battery I84 to wire I86 is then supplied to the electro-mag'nets 83 and 95 ofthe high and medium speed magnet valve devices, respectively, thereby energizing said electro-magnets. The energization 'of the high speed electro-magnet Bil-operates to seat thevalve 84 and to unseat the valve'85 thereby connecting the primary control pipe 81 to chamber 88, while the energization of the medium speed electro-magnet 95 acts to seatvalve 96 and unseat valve 91 so as to connect the primary control .pipe 81 to chamber 99. Under this speed condition the the primary control pipe medium speed magnet valve 91 and thence through passages I00 and IN to diagree, the spring I45- phragm I30 in a downwardly direction permitting valve device remains deenergized so that "the valve I08 remains seated and the valve I09 unseated. v

Fluid at the pressure supplied to the primary control pipe. 81 then flows past the unseated high speed magnet valve 85 to chamber 88, and thence through passage 89 to diaphragm chamber 62 Fluid-under pressure also flows from to chamber 99 phragm chamber 69, and also past the unseated low speed magnet valve I09 to chamber H0 and thence through passages III and H2 to diaphragm chamber II. Furthermore, fluid under pressure from the primary control pipe81 also flows directly through passage I22 and the several check valve chambers H1, H8 and M9 to diaphragm chamber 13.

,Under this high speed condition the fluid pressures are thus equalized on the opposite faces of the diaphragms 56, 51 and 58, but the diaphragm 55 is subjected to the differential of fluid pressures acting in chambers 62 and 59 and since at the time the application of brakes is initiated chamber 59 is at atmospheric pressure,

a force. is obtained on diaphragm 55 for effecting movement thereof toward the left hand.

The equalization of the fluid pressures on dia- 81 past the unseated phragm 56, 51 and 58 maintains same in a J balanced and therefore ineffective condition, but spring 14 acts upon movement of the diaphragm 55 to hold the other diaphragms in the engaging relation shown to avoid rattling and chafing thereof. Such equalization of pressures also prevents' subjecting the diaphragms 56, 51 and 58 to undue stresses under this'particular condition.

At the same time as fluid under pressure is supplied to the several diaphragm chambers as above described, fluid under pressure supplied from the primary control pipe 81 to the inshot valve chamber I38 flows past the unseated inshot valve I 3| to passage 93 and thence through port I34 to chamber I33 at the lower face of the inshotidiaphragm I30. At this time the release valve I32 is seated and. the magnet valves 96. I08 and 84 are also seated so that fluid under pressuresupplied to the diaphragm chamber I33 can not escape. As a consequence; when the pressure obtained in the diaphragm chamber I33 past the inshot valve I3I is built up suinciently to overcome the opposing pressure of spring I45, said diaphragm is deflected in an upwardly direction and permits spring, IM to seat theinshot valve I3I and'prevent furthersupply of fluid'under pressure to the chamber I33.

.The spring I45 is so related to the effective area of the flexible diaphragm I as to permit movement' of said diaphragm as just described when a relatively low pressure such as '1 pounds is obtainedin the diaphragm chamber I33. If for any reason the pressure of fluid obtained in chamber I33 should exceed this relatively low pressure of 7 pounds, then such excess pressure will cause further deflection of the diaphragm I30 in an upwardly direction and this movement will act through the stem I43 to unseat the release valve I32 to thereby release fluid under pressure from chamber I33. When the pressure of fluid in chamber I33 is thus reduced to a sufiicient dewill then move the diathe release valve 132 to close. In this manner the pressure of fluid Which it is possible to obtain in chamber I33 and acting on the'diaphragm I 33 is limited to a relatively low degree, such as '7 pounds, whenever an application of the brakes is effected and this is a very important feature in that it avoids over-stressing of said diaphragm and premature failure thereof. In this sameconnection it will also be noted that the travel of the diaphragm I 39 need only be sufficient to eflect unseating of the inshot valve I3I in one position and of the release valve I32 in the'opposite position, and therefore is held to a relativelylow degree which will also insure a relatively long operating life of the diaphragm. 1

When the diaphragm 55 is deflected toward the left hand as above described, it acts to shift plunger 41 and thereby the fulcrum pin for the floating'lever 44 in the same direction. The

pressure of spring 26 acting on the application pilot valve 25 is such as to hold the operating pin 2'! against movement upon the preliminary movement of plunger 41 just described and to thereby provide a fulcrum for the associated end of the lever 44, and as a consequence, the movement of the plunger 41 actuates the opposite end of said lever to first move the release pilot valve 36 relative to the release valve '29 and into seating engagement therewith after which further operation of the lever moves the release valve 29 into engagement with its seat 30.

After the release pilot valve 35 and the release valve 29 are thus both seated, they act through the pin 4I to provide a fulcrum for the assooiated end of the floating lever44 so that further movement of the plunger 41 in the direction of the left hand then actuates said leverlto shift the pin 21 in the direction of the application valve I5 to e'flect'unseating first of the pilotvalve 25 and then of the application valve I5. The unseating-of the release pilot valve 25 vents fluid under pressure from chamber 20 to chamber I3 at a rate substantially equal to the rate of supply through the relatively smallport :21, thereby reducing the force acting on the application valve I5 urging it to its seat so that a relatively low pressure of pin'2'I against the application valve I5 will unseat same against the opposing pressure of spring 23.

Unseating of the application valve I5 as 'just described opens communication between chamber I! and chamber I3 whereupon fluid at the pressure supplied by the feed valve device I to the pipe I9 flows to chamber I3 and thence through the secondary control pipe I4 to the brake cylinder device 5, thereby applying the brakeson the vehicle. i

The fluid pressure thus obtained in chamber I3 and acting in the brake cylinder device 5 flows through bore 60 in the relay valve device to chamber59 at the left hand face of the large diaphragm 55 and therein acts on said diaphragm in conjunction with therelatively light force of bias spring 65 to oppose the pressure provided in chamber 62 and acting on the opposite face of said diaphragm. Whenthis opposing pressure is increased sufficiently, due to the supply of fluid underpressure to chamber I3 and .to the brake cylinder device 5, to overcome the pressure of fluid in chamber 52, then the diaphragm 55 is deflected in the direction of the right hand and such movement operates through the plunger 41 and lever 44 to relieve the pressure of pin 21 on the application valve I5 and pilot valve 25. As a result, the spring 23 seats the application valve I5 "and the spring 26 seats the pilot valve 25 thereby cutting off the further supply of fluid aee'ase'e pperatesto supply fluid under pressure to chamber' I3 and from thence to the secondary control pipe Handbrake cylinder device 5 until the pressure of fluid obtained therein substantially equals that of the control pressure provided in the diaphragm-chamber 62.

It will therefore be evident that if a higher or lower pressure is provided in the primary control pipe 81 or if the pressure of fluid therein is increased to increase the degree with which the brakes are applied, the diaphragm 55 and the application and release valve device 9 will operate as'above described to provide a correspondingpressure in the secondary control pipe I4 and brake cylinder .device 5. It will also be noted that the large diaphragm 55 is the control diaphragm for the application and release valve device when thetrain-orvehicle is operating at or above the high speed limit of 6Qmiles per hour.

In order that the'application of brakes effected above'the high speed limit of 60 miles per hour will not cause slipping or sliding of the vehicle wheels as thespeed of the vehicle reduces, the governor device operates at the time the vehicle speed is reduced below said high speed limit to move the contactv I 53 out of engagement with the contact fingers Ifillthereby opening the circuit through and effecting deenergizatio'n of the high speed electro-magnet .83. As a result, spring 94 actsto seat the supply valve 85 and to unseat the valve =84, thereby disconnecting the diaphragm chamber 52 from the primary control pipe 87; and connecting same to therelease passage 93 leading to the inshot valve device I2.

Fluid under pressure then flows from the diaphragm chamber 62 @to the inshot valve device at a rate governed by choke .92, and as a-result, the pressure in chamber I33 acting on one face of the diaphragm I 30 is increased to above the opposing pressure of spring I45 and moves said diaphragm against said spring and unseats the release valve I32. Fluid under pressure in chamber '62 is then :released past the release valve I32 until reduced to a degree at which spring I45 predominates and moves the diaphragm I39 in a downwardly direction to permit seating of the release valve I32 under the action of spring I41. In this manner the pressure offluid in diaphragm Chamber'BZIis reduced to the relatively low degree, such as the 7 pounds above mentioned and provided for by the design ofthe inshot valve device. The pressure of fluid acting in the diaphragm chambers-:69, II and I3 of the relay valve device, however, remains the same as before movement of the governor contact I33 to its-open position. As a result, the diaphragms 51 and 58 remain in a balanced condition as to fluid pressures, while the diaphragm 55 is subjected to a differential of fluid pressures equal to the difference between those acting in chambers 62 The force now opposing that due to the pressure of fluid in chamber 59 'is equal to the force due to the -'differential between the fluid pressures in chambers "62 and '69 acting on diaphragm 53 "plus the force'due to the relatively low pressure of 7 pounds in chamber62 acting on the area of "the diaphragm v55.

As a result of this reduction in control force acting in the direction of the left hand the pressure of fluid in diaphragm chamber 59 obtained prior to the opening of governor switch contact vice 9 will again operate; as above described, to

I63 acts to move the diaphragm stack in the direction of the right hand. This movement of the diaphragm stack shifts the fulcrumpin 46 for the lever 44 in the same direction and rocks said lever in a counterclockwise direction about pin 50. As the lever 44 is thus operated it acts first to unseat the release pilot valve 36 from the release valve 29 so as to supply fluid under pressure from chamber Hi to chamber 33 wherein said pressure acts on the release valve piston 28 th substantially balance the fluid pressure in chamber I3 acting on the release valve-29 tending'to hold it seated. At about the same time as this condition is obtained, the nut 38 on the end of the release pilot valve stem 31 engages piston 28 so that further movement of the lever 44 acts to pull the release valve 29 from its seat whereupon fluid under pressure is vented from chamber I3 and thereby from the secondary control pipe 14 and brake cylinder device 5, and a corresponding reduction in pressure occurs in chamber .59.

This releasing of fluid under pressure from brake cylinder device 5 and diaphragm chamber 59 continues until the force of the fluid pressure acting'on the left hand face of the diaphragm becomes reduced to a degree slightly below the opposing control force of fluid pressure acting on the smaller diaphragm 56, at which time said control force effects movement of the plunger 41 in the direction of the left hand. This operation of the plunger again operates lever 44 to seat the pilot valve 36 against the release valve 29 andto then seat said release valve so as to thereby prevent the further release of fluid under pressure from chamber I3 and from the brake cylinder device 5. The pressure of fluid then remaining in the brake cylinder device isproportionallto that acting in chamber 69 on the diaphragm 56 the effective area of which is such as to limit the brake application on the vehicle to a degree which will minimize the danger of sliding of the vehicle wheels as the speed of the vehicle becomes reduced below the maximum speed limit of 60 miles per hour.

At the time the speed of the vehicle becomes further reduced to the medium speed limit of say 40 miles per hour, the collar I69 on the governor operating stem I59 engages the contact I64 so that any further reduction in speed moves said contact out of engagement with the contact fingers I6I. When this occurs the, electro-magnet 95 of the medium speed magnet valve device is deenergized which permits seating of valve 91 and unseating of valve 96. Upon unseating of valve 96 fluid under pressure in diaphragm chamber 69 is vented through passages IOI and I00, past said valve and through the release choke I03 to the release passage 93 leading to the inshot valve device I2.

The inshot valve device I2 then operates as hereinbefore described to release fluid under pressure from chamber 69 until such pressure is reduced to the relatively low degree of 7 pounds, above mentioned and which still is effective in diaphragm chamber 62. The diaphragm 56 is now in a balanced condition as to opposing fluid pressures. The pressure of fluid acting in diaphragm chambers H and 13 still remains, how ever, at the same degree as initially provided in the primary control pipe 81 and, as will be evident, the diaphragm 51 now becomes effective to control the pressure acting in the secondary control pipe I4 and in the brake cylinder device 5. Since the diaphragm 51 is, however, of less efiective area than diaphragm 56, the relay valve dereduce the'pressure in the'brake cylinder'device 5 to a value proportional to the area of diaphragm 56, thereby adjusting such pressure to the reduced speed of the train.

Now when the speed of the vehicle becomes further reduced to the low speed limit, say 20 miles per hour, the contact I- controlled by the governor device moves into engagement with the contact fingers I62 thereby supplying electric cur- Y rent from wire I86 to the electro-magnet I01 of the low speed magnet valve device. The electromagnet I01 is thereby energized and operates to unseat the valve I08 and to seat the valve I09. I The openingof valve I08 establishes communication between the diaphragm" chamber H and the release passage 93 by way of the release choke I I4 whereupon the inshot valve device I2 operates as hereinbefore'described to reduce the pressure in diaphragm chamber H to the relatively low degree of '7 lbs. which also remains effective in diaphragm chambers 69 and 62. The smallest diaphragm 58 of the diaphragm stack'now becomes efiective to control the operation of the application and release valve device 9 and since its effective areais less than that of diaphragm 51 which controlled the degree of brake application between the speed limits of 40 and 20 miles per hour, the relay valve device 9 will again operate to reduce the fluid pressure in the secondary control'pipe l4 and-brake cylinder device 5 to a degree which, acting in chamber 59 on the largest diaphragm 55, substantially counteracts that acting in chamber 13 on the smallest dia phragm 58. The degree of the brake application on the vehicle is therebyre-duced or adjusted to the relatively low speed limit of the vehicle and this degree of application will bemaintained'until the vehicle is brought to a stop.

If it is desired to effeot a complete release 01110 the brakes on the vehicle after the'vehicle is bnou-ght to a stop, the brake valve device 2 openated in the usual manner to completely release the fluid under pressure from the pmimary control pipe 81 and thereby fnom diarphnagmzg chamber 13 thnough the several check valve chambers H1, H8 and M9. The fluid pressure remaining in diaphragmchambers 62, 69 and 11 then unseats the check valves I24, I26 and I28,

respectively, and is dissipated through the pri- 50 m-ary con tnol pipe 81. The force urging the diaphragm stack toward the left hand is thereby relieved which permits the pressure of fluid acting in diaphragm chamber 59 to move the diaphragm stack in the direction of th right hand to .thereby open the release pilot valve 36 and release 'valve 29, as hereinbefore described, to permit a complete rel-ease of fiu'i-d under pressure from the secondary control pipe I 4 and from the brake cylinder device 5. The light bias spring 65 is provided to act on the plunger 41 at this time to bias'th'e diaphragm stack in. the direction of the right hand with a suflicient pressure to insure the complete release of fluid under pressure finom the secondary control pipe and from the brake cylinder device 5.

When the pressure of fluid in the primary contnol pipe 81 is reduced to a relatively low degree, such as one or two pounds, spring I19 in the switch device 4 acts to returnthe piston I15 .to its normal position shown to thereby move-the contact IiiI out of engagement with the contact fingers I82. The supply of electric current to the governor device is thereby cut ofi and the electro-magnet I01 of the low speed magnet valve device becomes deenergized permitting spring 6 to unseat the valve I69 and seat the valv I L8. All of the electro-magnet devices are now deenergized and in the same condition as before the brakes on the vehicle were applied, and this condition will be maintained until a subsequent application of the brakes is effected.

When fluid under pressure is vented from the several diaphragm chambers 62, 69 and 'II by way of the check valves I24, I26 and I28 as above described, the pressure of fluid in diaphragm chamber I33 of the inshot valve device I2 reduces by way of the unseated magnet valves 84, I68 and 9 6 and through said chambers and when thus reduced to a suincient degree the spring I45 moves the diaphragm I36 in. a downwardly direction to unseat the ins'hot valve I3I. After the in-shot valve I3I is thus unseated the further release of fluid under pressure from diaphragm chamber I33 and release passage 93 occurs through chamber I38 and the primary con trol pipe 81. The inshot valve device I2 is thus conditioned for a subsequent application of the brakes.

Let it be assumed that the brakes on the vehicle are released and the vehicle is operating at a speed below the high speed limit of 60 miles per hour but above the medium speed limit of 40 miles per hour, in which case the governor control cont-act I63 is open. If under this condition it is desired to effect an application of the brakes fluid under pressure is supplied to primary control pipe 81 as hereinbefore described and thence to the switch device 4 for effecting the operation of said switch device to supply electric current to the wire I86 and thence to the governor device. Current thus supplied to the governor device is supplied through the contact I64 to the medium speed el-ectro-magne't 95 and efiects energization thereof to seat valve 96 and to unseat valve 91. Since the governor contact I63 is out of engagement with the contact fingers I60 under this particular condition however, it will be noted that the high speed electr c-magnet 83 is not energized so that the valve 85 remains seated and the valve 84 unseated.

With the electric-magnet devices conditioned as just described, fluid under pressure supplied to the primary control pipe 81 flows past the inshot valve I3I to passage 93 and thence to chamber 9| in the high speed magnet valve device 80. From chamber 9-I fluid under pressure flows to chamber 88 and then through passages 89 and 90 to diaphragm chamber 62 between the largest diaphragm 5 5 and the adjacent, smaller diaphragm 56. This supply of fluid to diaphragm chamber 62 continues until the pressure obtained in diaphragm chamber I63 of the inshot valve device I2 is built up to a degree suflici-ent to overcome the opposing pressure of spring I45 at which time such diaphragm is deflected upwardly permitting seating of the inshot valve I3I. The inshot valve device thus limits the pressure of fluid obtained in diaphragm chamber 62 to the 7 lb. degree, above mentioned.

This relatively low pressure obtained in the diaphragm chamber 62 is adapted to efiect prompt movement of diaphragm 55 in the direction of the left hand and thereby prompt operation of the application and release valve device 9 to provide a corresponding pressure in the secondary control pipe I4 and in the brake cylinder device 5. This is an important feature in that it insures prompt movement of the brake shoes on the. vehicle into contact with the vehicle wheels.

At the same time as fluid under pressure is supplied to diaphragm chamber 62, as just described, fluid under pressure also flows from the primary control pipe '81 past the unseated medium speed magnet valve 91 to chamber 69 and thence through passages I 86 and IiiI' to chamber 59jbetween the diaphragms 56 and 51, and also from the primary control pipe past the low speed magnet valve I69 to passage III and thence to chamber II between the flexible diaphragms .51 and 58. Fluid under pressure also flows directly from the primary control pipe 87 through passage I22, check valve chambers H1, H8 and I I9 and passage I23 to chamber 73 at theright hand face of the smallest diaphragm 58. The fluid pressures acting on the opposite sides of the flexible diaphragms 51 and 56 are thereby equalized for reasons hereinbeiore described, while the fluid pressure obtained from the primary control pipe in chamber 69 acting on the diaphragm 56 is adapted to coact with the relatively low pressure obtained in diaphragm chamber 62 to effect operation of the application and release valve mechanism 92 to provide a proportionate pressure in the secondary control pipe I4 and brake cylinder device 5. The pressure of fluid thus obtained in the secondary control pipe and brake cylinder device is however limited by the relatively small effective area of diaphragm 58, in the same manner as above described, to a degree which will minimize the danger of sliding of the vehicle Wheels in the range of speed between the high and medium speed limits, such as 60 miles per hour and 40 milesper hour.

When, due to the application of brakes just described, the speed of the vehicle is reduced to a point slightly below the medium speed limit of 40 miles per hour, the speed governor device 3 acts to move the contact I64 out of engagement with the fingers I6I thereby effecting deenergization of the medium speed electromagnet 95, as a result of which the diaphragm chamber,

69 is placed in communication with the inshot valve device I2 which then operates to reduce the pressure therein to the same degree as acting in diaphragm chamber 62. The relay valve device is then controlled by the primary control pipe pressure acting in chamber II on the diaphragm 51 and is reflected in a reduction in pressure in the secondary control pipe I4 and in the brake cylinder device 5 to a degree corresponding to the reduced speed condition of the vehicle, in the same manner as hereinbefore described.

When the speed of the vehicle becomes further reduced to the low speed limit of 20 miles per hour, the governor device 3 effects engagement of the contact I65 with the contact fingers I62. The low speed electro-magnet I0! is thereby energized which connects the diaphragm chamber II to the inshot valve device I2. The inshot valve device then operates to reduce the pressure in chamber II to the '7 pound degree above described whereupon the primary control pipe pressure acting in diaphragm chamber 13 on the smallest diaphragm 58 acts to control the relay valve device and to permit a reduction in pressure in the secondary control pipe M and brake cylinder device 5 to a degree in accordance with the reduced vehicle speed, as above described. The pressure acting in chamber I3 on the smallest diaphragm 58 then controls the degree of brake application on the vehicle for all further reduction in vehicle speed.

Let it be assumed that at the time the brakes on the vehicle are applied the vehicle is operating at a speed between the medium and low speed limits of say 40 miles and 20 miles per hour. Under this condition the governor contacts I63 and I64 will be out of engagement with the contact fingers I60 and I6I and all of the magnet valve devices will therefore be deenergized at the time an application of the brakes is initiated. Under this condition fluid under pressure supplied to apply the brakes will flow from the primary control pipe 8! through the inshot valve device I2 to passage 93 and thence past the high speed magnet valve 84 to passage I66 leading to diaphragm chamber 62 and also past the medium speed magnet valve 96 to passage I60 leading to chamber 69, the pressure obtained in the diaphragm chambers 62 and 69 being limited by the operation of the inshot valve device, as hereinbefore described, to the relatively low degree such as 7 pounds.

This 7 pound pressure obtained in diaphragm chamber 62 acting on the large diaphragm 55 is adapted to efiect operation of said diaphragm and thereby of the application and release valve device 9 to effect a prompt supply of fluid under pressure to the secondary control pipe I4 and brake cylinder device to a like degree for efiecting movement of the brake shoes into engagement with the vehicle wheels. The fluid pressures are balanced on the opposite sides of the diaphragm 55 under this condition as will be apparent.

At the same time as fluid under pressure is supplied to diaphragm chambers 62 and 69'by way of the inshot valve device I2 as just described, fluid under pressure also flows from the primary control pipe 81 past the low speed magnet valve I69 to passage III and thence to diaphragm chamber II, and fluid under pressure also flows directly from the primary control pipe 81 to diaphragm chamber I3 on the outer face of the smallest diaphragm 58. The fluid pressures acting on the smallest diaphragm 58 are thereby equalized and the fluid pressure obtained in the diaphragm chamber II acting on the diaphragm 5! is adapted to control the. operation of the relay valve device 9 and to limit the pressure obtained in the brake cylinder device 5 to a degree corresponding to the relative small effective area of diaphragm 51 and therefore to the speed of the vehicle. In other words, if an application of the brakes is effected at the time the vehicle is operating between speeds of 40 and 20 miles an hour the diaphragm 51 is efiective to limit the brake application to a degree which will greatly reduce the danger of wheel sliding in this speed range.

When, due to the application of brakes just described, the speed of the vehicle becomes reduced to the low speed limit of 20 miles per hour, governor device 3 moves the contact I65 into contact with the contact fingers I62 and thereby efiects energization of the low speed electro-magnet III'I. The low speed electro-magnet valve I68 is thereby unseated and the valve I69 is seated and as a result, diaphragm chamber Ii is placed in communication with the inshot valve device I2 which then operates to reduce the pressure in said chamber to the relatively low degree of '7 pounds as hereinbefore described. The primary control pipe pressure in diaphragm chamber I3 acting on the smallest diaphragm 56 then becomes effective to limit the application of brakes on the vehicle, in the same manner as hereinbefore described, to a degree which will tend to avoid sliding of the wheels at and below the low speed limit of 20 miles per hour.

If at the time the'application of brakes on the vehicle is initiated the vehicle is operating at or below the low speed limit of 20 miles per hour, then both governor contacts I63 and I64 will be out of engagement with their respective contact fingers I60 and I6l, while the governor contact I65 will be bridging the contact fingers I62. The high and medium speed magnet valve devices will therefore remain deenergizedand the low speed magnet valve device will be promptly energized. Thus fluid under pressure supplied to the primary control device 81 and thence through the inshot valve device I2 will be supplied past the low speed magnet valve I08 to passage III and thence to diaphragm chamber II at the same time as it is supplied to the diaphragm chambers 62 and 69. As a result, the fluid pressures will be equalized on'diaphragms 56 and 51 and the relatively low pressure of 7 pounds obtained in cham ber 62 and acting on the largest diaphragm 55 will effect prompt operation of the application and release .valve device to provide a corresponding pressure in the secondary control pipe I4 and in brake cylinder device 5 in the same manner and for the same purpose as when the brakes are applied with the vehicle operating at a speed above the low speed limit, and as hereinbefore described. At the same time as fluid pressure is obtained in diaphragm chamber 62 for operating the largest diaphragm 55 fluid under pressure is also supplied from the primary control pipe 81 directly to diaphragm chamber I3 to act on the smallest diaphragm 58. The smallest diaphragm then operates to control the degree of pressure obtained in the secondary control pipe I5 and brake cylinder device 5, above that obtained from the fluid pressure provided in diaphragm chamber 62', and to limit such pressure to a degree corresponding to the relatively low speed of the vehicle.

From the above it will be noted that regardless of the speed at which the vehicle is operating at the time an application of the brakes is initiated onthe vehicle, fluid under pressure is always supplied to the diaphragm chamber 62 to act on the largest diaphragm 55 for initiating the operation of the application and release valve mechanism 9. This supply is by way of the high speed magnet valve device 80 whenever the speed of the vehicle is above the high speed limit at the time the brake application is initiated and at which time the inshot valve device I2 serves no useful function, however, whenever the speed of the vehicle is below the high speed limit at the time a brake application is initiated, this supply of fluid under pressure to chamber 62 is by way of the inshot valve device I2 and consequently limited to the relatively low degree of 7 pounds above mentioned. The importance of this feature will be brought out. An approximately '7 pounds per sq. in. fluid pressure is required in the brake cylinder device 5 to effect operation thereof to move the brake shoes on the vehicle into engagement with the vehicle wheels and it is desired that this movement be effected promptly to avoid undue rattling and vibration of the shoes, and brake rigging carrying same, during movement thereof between their release positions and their application positions. A relatively low degree of pressure, such as 7 pounds, in chamber 62 acting on the relatively large area of diaphragm 55 will provide a like pressure in the brake cylinder device which will effect prompt movement of the brake shoes into engagement with the wheels as just described. However, the same degree of pressure acting on any of the other diaphragms could not provide such prompt movement due to the less effective area of the diaphragms and, as a consequence, the lower force for operating the application and release valve mechanism 9 to its brake applying position.

In other words, consider the extreme diaphragms 55 and 53 of the stack and assume that the diaphragm 58 has four tenths the effective area of diaphragm 55. Now '7 lbs. pressure in chamber 62 will provide a like pressure in brake cylinder devices for moving the brake shoes into engagement with the vehicle wheels as desired, but the same degree of fluid pressure acting in chamber '53 on diaphragm 58 will provide only four-tenths the amount of pressure in the brake cylinder device and therefore less than one-half that required for moving the shoes into engagement with the wheels. It will be therefore apparent that if the diaphragm 58 controlled movement of the shoes into engagement with the wheels it would require approximately 17 lbs. pressure in diaphragm chamber 73 for actuating the diaphragm 58. Obviously it would take a greater period of time to obtain 17 lbs. pressure in chamber 13 than 7 lbs. pressure in the diaphragm chamber 62, so that if the diaphragm 58 were effective to control the movement of the brake shoes against the wheels such movement would be delayed and unduly slow resulting in rattling and vibration, such as above described. Such rattling and vibration is however minimized with the improved structure since, regardless of the condition of the vehicle as to speed at the time an application of brakes is initiated, a sufficient degree of pressure is provided in diaphragm chamber 62 to act on the largest diaphragm 55 to insure prompt movement of the brake shoes against the wheels. After this initial supply of fluid pressure to the brake cylinder device the further supply of fluid to the rake cylinder device is limited to a pressure dependent upon which of the diaphragms 55, 5t, 5"! or 5B is effective at the time.

It will :be noted that whenever the brakes on the vehicle are applied all of the diaphragms 55, 5B, 5'! and 5B are subject to fluid pressure, the diaphragm or diaphragms to the right of the control diaphragm above the low speed limit being subject to the same degree of fluid pressure as the control diaphragm, while below the high speed limit, the diaphragm or diaphragms to the left of the control diaphragm are subject to the pressure of fluid supplied by the inshot valve device. This is important in that it prevents undue stressing or buckling of the diaphragms and it also insures that the diaphragms will be held in cooperative relation at all times to prevent chafing of the parts and to prevent the follower plates between the diaphragms from shifting from their operating positions.

In the operation of the magnet valve devices to vent fluid under pressure from the various diaphragm chambers as the speed of the vehicle reduces it will be noted that one or another of the release chokes its, l l 4 and 92 controls the rate of such release and also the rat-e at which such fluid pressure is supplied to the inshot valve device 52. A slight increase in pressure obtained in the inshot valve device l2 on the diaphragm 139 by such supply then operates said diaphragm to effect unseating of the release valve I32 to release the fluid pressure from diaphragm chamber l 30 so as to limit the increase in pressure on said diaphragm. By this arrangement it will be evident that the pressure of fluid obtained in chamber #33 acting on diaphragm l3ll will never materially exceed the opposing pressure'of the control spring [65. By thus limiting the pressure obtainable on the diaphragm I30 to a relatively low degree and limiting the movement of the diaphragm, as hereinbefore described, undue stressing of this diaphragm is avoided and relatively long life thereof is assured.

It will now be seen that, regardless of the control pressure provided in the primary control pipe 87 by the operator, the improved brake equipment will provide in the secondary control pipe l4 and in the brake cylinder device 5 a pressure which is proportionate thereto and to the speed of the vehicle and will automatically reduce the pressure acting in. the secondary control pipe l4 and in the brake cylinder device 5, as the speed of the vehicle reduces, for the purpose of minimizing the danger of slipping or sliding of the vehicle wheels, and without any change in pressure in the primary control pipe 81 by the operator. It will also be seen that operation of the brake cylinder device 5 to effect prompt movement of the brake shoes into engagement with the vehicle wheels upon initiating an application of the brakes on the vehicle is assured regardless of which of the diaphragms is effective to control the degree of the application.

While one illustrative embodiment of the invention has been described in detail, it is not the intention to limit the scope to that embodiment or otherwise than by the terms of the appended claims.

Having now described my invention, what I claim as new and desire to secure :by Letters Patent, is:

1. In a vehicle brake system, in combination, means having a plurality of chambers, valve means operative in accordance with variations in fluid pressure in said chambers for controlling the degree of brake application on the vehicle, supply means for supplying fluid under pressure for effecting an application of the brakes on the vehicle, pressure limiting means for supplying fluid from said supply means at a pressure which is less than supplied by said supply means, and means controlled by a variable operating condition of the vehicle for selectively connecting, in accordance with changes in said operating condition, one or more of said chambers to said supply means and the other chamber or chambers to said pressure limiting means.

2. In a vehicle "brake system, in combination, means having a plurality of chambers, valve means operative in accordance with variations in fluid pressure in said chambers for controlling the degree of brake application on the vehicle, supply means for supplying fluid under pressure for effecting an application of the brakes on the vehicle, pressure limiting means for supplying fluid from said supply means at a pressure which is less than supplied by said supply means, and means controlled by a variable operating condition of the vehicle for selectively connecting, in accordance with changes in said operating condition, one or more of said chambers to said supply means and at least one of said chambers to said pressure limiting means.

3. In a vehicle brake system, in. combination, means having a plurality of chambers, valve means operative in accordance with variations in fluid pressure in said chambers for controlling the degree of brake application on the vehicle, supply means for supplying fluid under pressure for efiecting an application of the brakes on the vehicle, pressure limiting means for supplying fluid from said supply means at a pressure which is less than supplied .by said supply means, and means controlled by a variable operating condition of the vehicle operative at one time to connect all of said chambers to said supply means and operative at other times, according to different changes in said operating condition, to selectively disconnect one or more of said chambers from said supply means and to connect same to said pressure limiting means.

4. In a vehicle brake system, in combination, means having a plurality of chambers, valve means operative in accordance with variations in fluid pressure in said chambers for controlling the degree of brake application on the vehicle, supply means for supplying fluid under pressure for effecting an application of the brakes on the vehicle, means controlled by a variable operating condition of the vehicle for selectively connecting, in accordance with changes in said operating condition, one or more of said chambers to said supply means, and pressure limiting means operative independently of the operating condition I of the vehicle and controlling the supply of fluid under pressure from said supply means to one of said chambers and operative to cut ofi said supply upon an increase in pressure therein to a chosen degree which is less than supplied by said supply means.

5. In a vehicle brake system, in combination, means having a plurality of chambers, valve means operative in accordance with variations in fluid pressure in said chambers for controlling the degree of brake application on the vehicle, supply means for supplying fluid under pressure to each of said chambers through a separate communication, pressure limiting means for supplying fluid from said supply means at a pressure which is less than supplied by said supply means, and means controlled by a variable operating condition of the vehicle and operative upon a series of successive changes in such condition to close first one and then another of said communications and at the same time to suc cessively connect the chambers thus cut off from said supply means to said pressure limiting means for rendering said pressure limiting means operative to control the pressure therein.

6. In a vehicle brake system, in combination, means having a plurality of chambers, valve means operative in accordance with variations in fluid pressure in said chambers for controlling the degree of brake application on the vehicle,

supply means for supplying fluid under pressure to each of said chambers through a separate communication, pressure limiting means for supplying fluid from said supply means at a pressure which is less than supplied by said supply means, and valve means controlled by a variable operating condition of the vehicle and operative in accordance with different changes in said operating condition to close one or more of said communications and to connect the chamber or chambers thus cut off from said supply means to said pressure limiting means for rendering said pressure limiting means operative to control the pressure therein.

7. In a vehicle brake system, in combination, means having a plurality of chambers, valve means operative in accordance with variations in pressure in said chambers for controlling the degree of brake application on the vehicle, supply means for supplying fluid under pressure to each of said chambers through a separate communication, a pressure limiting device operative upon the supply of fluid under pressure by said supply means to supply fluid under pressure to a secondary chamber and to release fluid under pressure therefrom for providing therein a substantially constant pressure, and means controlled by a variable operating condition of the vehicle controlling said communications and operative in accordance with different changes in said operating condition to close one or more of said communications and to connect the chamber or chambers thus cut off from said supply means to said secondary chamber whereby said pressure limiting means is rendered effective to limit the pressures therein.

8. In a vehicle brake system, in combination, a pair of cooperatively arranged movable abutments of different effective areas adapted to be operated by fluid under pressure to effect an application of the brakes, supply means for supplying fluid under pressure to both of said abutments for actuating same, and means operative to limit the pressure of fluid supplied to actuate the larger of the two abutments to a degree less than supplied by said supply means.

9. In a vehicle brake system, in combination, a pair of cooperatively arranged movable abutments of different effective areas adapted to be operated by fluid under pressure to effect an application of the brakes, supply means for supplying fluid under pressure to both of said abutments for actuating same, pressure limiting means for supplying fluid from said supply means at a pressure which is less than supplied by said supply means, and a valve device controlled by a variable operating condition of the vehicle controlling communication through which fluid is adapted to be supplied from said supply means to the abutment of greater area and operative upon a change in such condition to close said communication and to connect said abutment of greater area to said pressure limiting means for control by the pressure of fluid supplied by said pressure limiting means.

10. In a vehicle brake system, in combination, a pair of cooperatively arranged movable abutments of different effective areas adapted to be operated by fluid under pressure to effect an ap plication of the brakes,'supply means for supplying fluid under pressure to both of said abutments for actuating same, means operative upon the supply of fluid under pressure by said supply means to supply fluid under pressure to and to release fluid under pressure from a chamber for providing a substantially constant pressure therein, and means controlled by a variable operating condition of the vehicle and operative upon a change in such condition to close communication between said supply means and the abutment of larger area and to connect said abutment of larger area to said chamber for control by the fluid pressure therein.

11. In a vehicle brake system, in combination,

the supply of fluid under pressure to said supply means to supply fluid to a chamber at a pressure which is less than in said supply means, means controlled by a variable operating condition of the vehicle controlling the supply of fluid under pressure from said supply means to said abutments and operative in accordance With various changes in said operating condition to selectively close communication between said supply means and one or more of said abutments and to connect the abutment of greatest eflective area to said chamber for control by the fluid pressure therein.

12. In a vehicle brake system, in combination, a secondary control pipe, a pair of movable abutments of different efiective areas, valve means controlled by the pressure of fluid acting on said abutments for providing a proportional pressure in said secondary control pipe for applying the brakes on the vehicle, a primary control pipe to which fluid under pressure is adapted to be supplied for controlling the operation of said abutments, the outer face of the larger of said abutments being subject to pressure of fluid in said secondary control pipe and the opposite face of the other abutment being connected to said primary control pipe, means operative upon the supply of fluid under pressure to said primary control pipe to supply fluid to a chamber at a pressure which is less than in said primary control pipe, and means controlled by a variable operating condition of the vehicle operative at one time to establish communication between the primary control pipe and the adjacent faces of the two abutments and at another time to close said communication and to establish a communication between said chamber and the acjacent faces of the two abutments.

13. In a vehicle brake system, in combination, a secondary control pipe, a pair of movable abutments of different effective areas, valve means controlled by the pressure of fluid acting on said abutments for providing a proportional pressure in said secondary control pipe for applying the brakes on the vehicle, a primary control pipe to which fluid under pressure is adapted to be supplied for controlling the operation of said abutments, the outer face of the larger of said abutments being subject to pressure of fluid in said secondary control pipe and the opposite face of the other abutment being connected to said primary control pipe, said abutments cooperating to form a pressure chamber intermediate thereof, limiting valve means operative upon the supply of fluid under pressure to said primary control pipe to supply fluid under pressure to and to release fluid under pressure from another chamber, a spring, a movable abutment controlled by the opposing pressures of said spring and the pressure of fluid in said other chamber for controlling the operation of said limiting valve means to provide a limited pressure in said other chamber which is less than in said primary control pipe, and means operativeunder one operating condition of the vehicle to connect the chamber intermediate said abutments to said primary control pipe and under operatively associated with said valve means for controlling the operation thereof, said diaphragm being subject on their adjacent faces to the pressure of fluid in an intermediate chamber normally open to said primary control pipe, one of said diaphragms being subject on its opposite face to the pressure of fluid in said secondary control pipe and the other diaphragm being subject on its opposite face to the pressure of fluid in a chamber which is open to said primary control pipe, means for supplying fluid under pressure through said primary control pipe to both of said chambers for effecting operation of said valve means to supply fluid under pressure to said secondary control pip-e, a valve controlling communication between said primary control pipe and the chamber formed intermediate said diaphragms, means responsive to a certain operating condition of the vehicle for operating said valve to open said communication and to a diiTerent operating condition of the vehicle to operate said valve to close said communication and to connect said intermediate chamber to a release passage for releasing fluid under pressure therefrom, a spring, and valve means controlled by opposing pressures of fluid in said release passage and said spring and operative to either supply fluid under pressure from said primary control pipe to said release passage or for releasing fluid under pressure from said release passage to maintain a chosen degree of pressure in said release passage Which is less than in said primary control pipe.

15. In a vehicle brake system, in combination, a primary control pipe, a secondary control pipe, valve means operative to supply fluid under pressure to and to release fluid under pressure from said secondary control pipe, a stack of cooperatively arranged, flexible diaphragms of successively decreasing effective areas operatively connected to said valve means for controlling the operation thereof, the stack being arranged with the outer face of the largest diaphragm subject to pressure in said secondary control pipe and the opposite face of the smallest diaphragm subject to the pressure of fluid in said primary control pipe, there being provided between each adjacent pair of said diaphragms an intermediate chamber, means controlled by a variable operating condition of the vehicle for controlling communication between the several intermediate chambers and said primary control pipe and operative at one time to connect all of said intermediate chambers to said primary control pipe and operative at other times to disconnect one or more of said intermediate chambers from said primary control pipe and to connect same to a release communication, and a pressure limiting device operative upon the supply of fluid under pressure to said primary control pipe to supply fluid to said release passage at a chosen pressure which is less than in said primary control pipe and operative upon an increase in pressure in said release passage to a degree greater than said chosen pressure to release fluid under pressure therefrom.

16. In a control device for a fluid pressure brake system, in combination, a stack of cooperating unconnected movable abutments of different eifective areas arranged in coaxial spaced relation and adapted to move collectively as a unit, means for supplying fluid under pressure to the spaces intermediate said abutments and to the space at the outer face of one of the end abutments of said stack for efiecting movement of said stack out of a normal position, means for selectively varying the degree of fluid pressure acting in said intermediate spaces, valve means controlled by movement of said abutments and connected to the abutment at the opposite end of said stack for movement therewith, and a spring acting on the first named end abutment for urging all of said abutments in the direction of the last named end abutment to maintain all of said abutments in operating contact.

17. In a control device for a fiuid pressure brake system, in combination, a stack of cooperating unconnected movable abutments of different effective areas arranged in coaxial spaced relation and adapted to move collectively as a unit, means for supplying fluid under pressure to the spaces intermediate said abutments and to the space at the outer face of one of the end abutments of said stack for efiecting movement of said stack out of a normal position, means for selectively varying the degree of fluid pressure acting in said intermediate spaces, valve means controlled by movement of said abutments and connected to the abutment at the opposite end of said stack for movement therewith, a spring ELLIS E. HEWITT. 

